CA1250749A - Heat recovery system - Google Patents
Heat recovery systemInfo
- Publication number
- CA1250749A CA1250749A CA000518328A CA518328A CA1250749A CA 1250749 A CA1250749 A CA 1250749A CA 000518328 A CA000518328 A CA 000518328A CA 518328 A CA518328 A CA 518328A CA 1250749 A CA1250749 A CA 1250749A
- Authority
- CA
- Canada
- Prior art keywords
- high pressure
- steam
- exhaust
- feedwater heater
- process according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
- F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
- F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
- F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A gas turbine heat recovery system that can be used in steam reforming plants is disclosed. The system utilizes a high pressure steam superheater and a high pressure feedwater heater to recover the heat from the exhaust gas turbine.
A gas turbine heat recovery system that can be used in steam reforming plants is disclosed. The system utilizes a high pressure steam superheater and a high pressure feedwater heater to recover the heat from the exhaust gas turbine.
Description
~25V74~
HEAT RECOVERY SYSTEM
This invention relates to a heat recovery system. In particular it relates to a heat recovery system for gas turbine exhaust. In a specific embodiment it relates to a heat recovery system for gas turbine exhaust in a steam reforming plant.
Many process plants have been built incorporating steam systems operating at evaporation pressures of around lO0 atmo-spheres. Most of these plants are used to produce ammonia syn-thesis gas by the steam reforming of natural gas.
The main reason for adopting this rather high steam generation pressure in these plants, relative to contemporary process plant practice of 40-60 atmospheres, is that about half the steam generated in these plants is needed at around 40 atmo-spheres for the steam reforming process, and a substantial amount of power can be produced by expansion of the steam from a higher pressure to this extraction pressure of around 40 atmospheres.
The balance of the steam is used in condensing steam turbines, mainly driving compressors and pumps.
Many industries that need both electric power and pro-cess heat are installing so-called gas turbine cogeneration sys-tems. Most of these consist of a gas-fired open cycle gas tur-bine generating electricity, with the turbine exhaust at about 1000F passing through a waste heat boiler to generate steam.
The high thermal efficiency of these cogeneration plants, which can exceed 70%, allows them to produce electric power and process heat at low cost.
~&
~Z5q)~749 In these cogeneration plants, the gas turbine exhaust at about lOOO"F is first used to generate ~and sometimes to superheat) process steam. The generation pressure is normally under 40 atmospheres. The exhaust gases are then used to gener-ate further steam at low pressure. This is used for boiler feed-water heating and deaerating, and occasionally in a steam tur-bine. The cooled exhaust gas leaves the waste heat boiler at 250 to 300F.
Studies have been made on installing these gas turbine cogeneration systems on the large steam reforming plants referred to above, with integration of the gas turbine heat recovery with the existing lO0 atmosphere steam systems. At first sight, this would improve the economics of operation, through generation of electric power for plant use at high thermal efficiency.
There is however a problem with this concept, arising from the evaporation temperatures of around 600F associated with 100 atmosphere steam generation. The proportion of the heat available in the gas turbine exhaust at 1000F that can be used for high pressure steam generation is thus quite limited. The lowest exhaust temperature at the outlet of the high pressure feedwater heater is around 500F, and heat recovery beneath that temperature level to low pressure steam generation represents a low grade of heat recovery.
~2St~
The instant invention allows a higher proportion of the heat available in the gas turbine exhaust to be used for the pro-duction of 100 atmosphere steam or steam at similar high pres-sures.
SUMMARY OF T~E INVENTION
According to the instant invention, gas turbine exhaust is passed through a waste heat exchanger consisting of a high pressure steam superheater and a high pressure feedwater heater, where the exhaust gas first contacts the high pressure steam su-perheater and then contacts the high pressure feedwater heater.
This invention is also directed to a process for producing high pressure steam using gas turbine exhaust, a waste heat exchanger-and a separate evaporator comprising passing the exhaust through the waste heat exchanger where the exhaust first contacts a high pressure steam superheater and then contacts a high pressure feedwater heater.
This invention is îurther ~irected ~o a heat recovery system comprising a gas turbine, a waste heat exchanger and a separate evaporator where said waste heat exchanger consists of a means for passing exhaust gas from the turbine to the exchanger, the exchanger containing a high pressure steam superheater and a high pressure feedwater heater. This combination allows for an in-creased production of high pressure steam in the complete steam system over prior art gas turbine heat recovery sys~ems employing ~aste heat boilersO
-4- l;~S~)7'~
BRIEF DESCRIPTION OF THE D AWINGS
Figure 1 shows a schematic view of an example of the instant invention's heat recovery system.
Figure 2 show a schematic view of another example of the instant invention's heat recovery system in a steam reforming plant.
DESCRIPTION O~ THE PREFERRED EMBODIMENT ~;
According to the instant invention, and as shown by example in Figure 1, gas turbine exhaust from gas turbine 7, which is at a temperature ranging from about 900 deg. to about 1200 deg. F, but preferably around 1000 deg. F, enters into a waste heat exchanger 1. There it contacts a high pressure steam superheater 2 through which is passed saturated steam from a steam generator, 8. The steam is at elevated pressures ranging from about 90 to 150 atmospheres but preferably around 100 atmospheres and a temperature generally around about 550 deg. to about 650 deg. F. Although the steam flow rate can be any suitable flow rate, generally the flow rate will range from about 50,000 pounds per hour to about 150,000 pounds per hour. The steam generator can be any type of evaporator system, such as a stream drum in a reformer unit. This steam is superheated in a high pressure steam superheater 2, ~ith the exhaust of the gas turbine, to steam at a temperature of around 800 deg~ to about 1000 deg. F, depending upon the temperature of the gas turbine exha~st.
~ZS~9 The gas turbine exhaust then contacts high pressure feedwater heater 3 in which water is heated from a temperature ranging from about 200 deg. to about 500 deg. F to a temperature ranging from about 400 deg to about 600 deg. F. The high pressure feedwater heater is maintained at a pressure ranging from about 90 to about 150 atmospheres. Any suitable flow rate can be used with this heater, but generally the flow rate ranges from about 400,000 to about 600 ,oon pounds per hour.
The gas turbine exhaust, as shown in Figure 2, can then be 10 contacted with exchan~ers such as a feed gas heater 4, a fuel gas heater 5 and a low pressure feedwater heater 6. The gas turbine exhaust can also contact a second high pressure feedwater heater, a steam/deaerated water heater, or any other type of exchanger.
The gas turbine exhaust then exits the waste heat exchanger at a 15 temperature ranging from about 250 deg to about 450 deg. F.
The use of the high pressure superheater 2 replaces the combination of superheater and evaporator, in series on the steam side, that is usually used in waste heat boilers. This eliminates the need for extra high pressure steam drums and circulating pumps, 20 and also affords improved control over the temperature of the overall plant superheated steam supply to the turbines.
1~5t~ 9 Additionally, the high pressure boiler feedwater that is heated in the high pressure feedwater heater 3 with the gas turbine exhaust is then evaporated in a separate evaporator 8, outside the subject waste heat exchanger. The saturated steam thus produced is then heated in high pressure steam superheater 2 to form superheated steam. The feedwater heater 3, replaces the low pressure steam generation system that is normally used in prior waste heat boilers and contributes directly to the amount of high pressure steam produced elsewhere in the plant. This was not the case with the low pressure steam generation system.
THEORET I CAL EXAMP LE
This example of the invention is shown in Figure 2.
Gas turbine exhaust enters a multi-service heat exchanger provided with five heat-exchange surfaces, numbered from 2 to 6, which recover heat for use in an adjacent ammonia plant. The cooled exhaust gas is then discharged to the atmo-sphere.
At the base of the exchanger, 571,417 lb/hr of gas tur-bine exhaust enters the exchanger at a temperature of 986F. The exhaust first passes over high pressure steam superheater, in which 100,000 lb/hr of 1550 p.s.i.g. saturated steam is heated from 603F to 860F. The heat removed is 23.7 mm aTu/hr.
The exhaust, which is now at a temperature of 836F, next passes over high pressure feedwater heater 3 in which 492,720 lb/hr of boiler feed water at 2,000 p.s.i.g. and 427F is heated to 523F. The heat removed is 53.5 mm BTU/hr.
The exhaust, now at a tem~erature of 479F, passes over feed gas heater 4, in which 25~3 lb mol~hr of na';ural gas at 60~
p.s.i.g. and 55F .s heated to 420F. The heat removed is 8.9 mm BTU/hr.
The exhaust at a temperature of 418F passes over fuel ~as heater 5, in which 1678 lb mol/hr of natural gas at 300 p.s.i.q. and 55F is heated to 360F. The heat removed is 4.8 mm gTu/hr.
Finally, the exhaust at a temperature of 38S passes over low pressure feedwater heater 6, in which 168,000 lb~hr of boiler feedwater at 120 p.s.i.g. and 240F is heated to 300F.
The heat removed-is 10.3 mm BTU/hr and the exhaust gas is dis-charged to the atmosphere at 314F.
The total of the heat recovered in the five heatexchange surfaces is thus 101.2 mm ~TU/hr.
It is to be understood that the heat exchange surfaces described above can be interleaved if desired, so as to achieve a more economical use of constructional materials, and consequently the inter-surface temperatures given are subject to some varia-tion.
This example is intended to be exemplary. Other embod-iments within the scope of this inven~ion are intended to be included.
HEAT RECOVERY SYSTEM
This invention relates to a heat recovery system. In particular it relates to a heat recovery system for gas turbine exhaust. In a specific embodiment it relates to a heat recovery system for gas turbine exhaust in a steam reforming plant.
Many process plants have been built incorporating steam systems operating at evaporation pressures of around lO0 atmo-spheres. Most of these plants are used to produce ammonia syn-thesis gas by the steam reforming of natural gas.
The main reason for adopting this rather high steam generation pressure in these plants, relative to contemporary process plant practice of 40-60 atmospheres, is that about half the steam generated in these plants is needed at around 40 atmo-spheres for the steam reforming process, and a substantial amount of power can be produced by expansion of the steam from a higher pressure to this extraction pressure of around 40 atmospheres.
The balance of the steam is used in condensing steam turbines, mainly driving compressors and pumps.
Many industries that need both electric power and pro-cess heat are installing so-called gas turbine cogeneration sys-tems. Most of these consist of a gas-fired open cycle gas tur-bine generating electricity, with the turbine exhaust at about 1000F passing through a waste heat boiler to generate steam.
The high thermal efficiency of these cogeneration plants, which can exceed 70%, allows them to produce electric power and process heat at low cost.
~&
~Z5q)~749 In these cogeneration plants, the gas turbine exhaust at about lOOO"F is first used to generate ~and sometimes to superheat) process steam. The generation pressure is normally under 40 atmospheres. The exhaust gases are then used to gener-ate further steam at low pressure. This is used for boiler feed-water heating and deaerating, and occasionally in a steam tur-bine. The cooled exhaust gas leaves the waste heat boiler at 250 to 300F.
Studies have been made on installing these gas turbine cogeneration systems on the large steam reforming plants referred to above, with integration of the gas turbine heat recovery with the existing lO0 atmosphere steam systems. At first sight, this would improve the economics of operation, through generation of electric power for plant use at high thermal efficiency.
There is however a problem with this concept, arising from the evaporation temperatures of around 600F associated with 100 atmosphere steam generation. The proportion of the heat available in the gas turbine exhaust at 1000F that can be used for high pressure steam generation is thus quite limited. The lowest exhaust temperature at the outlet of the high pressure feedwater heater is around 500F, and heat recovery beneath that temperature level to low pressure steam generation represents a low grade of heat recovery.
~2St~
The instant invention allows a higher proportion of the heat available in the gas turbine exhaust to be used for the pro-duction of 100 atmosphere steam or steam at similar high pres-sures.
SUMMARY OF T~E INVENTION
According to the instant invention, gas turbine exhaust is passed through a waste heat exchanger consisting of a high pressure steam superheater and a high pressure feedwater heater, where the exhaust gas first contacts the high pressure steam su-perheater and then contacts the high pressure feedwater heater.
This invention is also directed to a process for producing high pressure steam using gas turbine exhaust, a waste heat exchanger-and a separate evaporator comprising passing the exhaust through the waste heat exchanger where the exhaust first contacts a high pressure steam superheater and then contacts a high pressure feedwater heater.
This invention is îurther ~irected ~o a heat recovery system comprising a gas turbine, a waste heat exchanger and a separate evaporator where said waste heat exchanger consists of a means for passing exhaust gas from the turbine to the exchanger, the exchanger containing a high pressure steam superheater and a high pressure feedwater heater. This combination allows for an in-creased production of high pressure steam in the complete steam system over prior art gas turbine heat recovery sys~ems employing ~aste heat boilersO
-4- l;~S~)7'~
BRIEF DESCRIPTION OF THE D AWINGS
Figure 1 shows a schematic view of an example of the instant invention's heat recovery system.
Figure 2 show a schematic view of another example of the instant invention's heat recovery system in a steam reforming plant.
DESCRIPTION O~ THE PREFERRED EMBODIMENT ~;
According to the instant invention, and as shown by example in Figure 1, gas turbine exhaust from gas turbine 7, which is at a temperature ranging from about 900 deg. to about 1200 deg. F, but preferably around 1000 deg. F, enters into a waste heat exchanger 1. There it contacts a high pressure steam superheater 2 through which is passed saturated steam from a steam generator, 8. The steam is at elevated pressures ranging from about 90 to 150 atmospheres but preferably around 100 atmospheres and a temperature generally around about 550 deg. to about 650 deg. F. Although the steam flow rate can be any suitable flow rate, generally the flow rate will range from about 50,000 pounds per hour to about 150,000 pounds per hour. The steam generator can be any type of evaporator system, such as a stream drum in a reformer unit. This steam is superheated in a high pressure steam superheater 2, ~ith the exhaust of the gas turbine, to steam at a temperature of around 800 deg~ to about 1000 deg. F, depending upon the temperature of the gas turbine exha~st.
~ZS~9 The gas turbine exhaust then contacts high pressure feedwater heater 3 in which water is heated from a temperature ranging from about 200 deg. to about 500 deg. F to a temperature ranging from about 400 deg to about 600 deg. F. The high pressure feedwater heater is maintained at a pressure ranging from about 90 to about 150 atmospheres. Any suitable flow rate can be used with this heater, but generally the flow rate ranges from about 400,000 to about 600 ,oon pounds per hour.
The gas turbine exhaust, as shown in Figure 2, can then be 10 contacted with exchan~ers such as a feed gas heater 4, a fuel gas heater 5 and a low pressure feedwater heater 6. The gas turbine exhaust can also contact a second high pressure feedwater heater, a steam/deaerated water heater, or any other type of exchanger.
The gas turbine exhaust then exits the waste heat exchanger at a 15 temperature ranging from about 250 deg to about 450 deg. F.
The use of the high pressure superheater 2 replaces the combination of superheater and evaporator, in series on the steam side, that is usually used in waste heat boilers. This eliminates the need for extra high pressure steam drums and circulating pumps, 20 and also affords improved control over the temperature of the overall plant superheated steam supply to the turbines.
1~5t~ 9 Additionally, the high pressure boiler feedwater that is heated in the high pressure feedwater heater 3 with the gas turbine exhaust is then evaporated in a separate evaporator 8, outside the subject waste heat exchanger. The saturated steam thus produced is then heated in high pressure steam superheater 2 to form superheated steam. The feedwater heater 3, replaces the low pressure steam generation system that is normally used in prior waste heat boilers and contributes directly to the amount of high pressure steam produced elsewhere in the plant. This was not the case with the low pressure steam generation system.
THEORET I CAL EXAMP LE
This example of the invention is shown in Figure 2.
Gas turbine exhaust enters a multi-service heat exchanger provided with five heat-exchange surfaces, numbered from 2 to 6, which recover heat for use in an adjacent ammonia plant. The cooled exhaust gas is then discharged to the atmo-sphere.
At the base of the exchanger, 571,417 lb/hr of gas tur-bine exhaust enters the exchanger at a temperature of 986F. The exhaust first passes over high pressure steam superheater, in which 100,000 lb/hr of 1550 p.s.i.g. saturated steam is heated from 603F to 860F. The heat removed is 23.7 mm aTu/hr.
The exhaust, which is now at a temperature of 836F, next passes over high pressure feedwater heater 3 in which 492,720 lb/hr of boiler feed water at 2,000 p.s.i.g. and 427F is heated to 523F. The heat removed is 53.5 mm BTU/hr.
The exhaust, now at a tem~erature of 479F, passes over feed gas heater 4, in which 25~3 lb mol~hr of na';ural gas at 60~
p.s.i.g. and 55F .s heated to 420F. The heat removed is 8.9 mm BTU/hr.
The exhaust at a temperature of 418F passes over fuel ~as heater 5, in which 1678 lb mol/hr of natural gas at 300 p.s.i.q. and 55F is heated to 360F. The heat removed is 4.8 mm gTu/hr.
Finally, the exhaust at a temperature of 38S passes over low pressure feedwater heater 6, in which 168,000 lb~hr of boiler feedwater at 120 p.s.i.g. and 240F is heated to 300F.
The heat removed-is 10.3 mm BTU/hr and the exhaust gas is dis-charged to the atmosphere at 314F.
The total of the heat recovered in the five heatexchange surfaces is thus 101.2 mm ~TU/hr.
It is to be understood that the heat exchange surfaces described above can be interleaved if desired, so as to achieve a more economical use of constructional materials, and consequently the inter-surface temperatures given are subject to some varia-tion.
This example is intended to be exemplary. Other embod-iments within the scope of this inven~ion are intended to be included.
Claims (13)
1. A process for recovering heat from gas turbine exhaust comprising passing said exhaust through a waste heat exchanger consisting of a high pressure steam superheater and a high pressure feedwater heater where said exhaust gas first con-tacts said high pressure steam superheater and then contacts said high pressure feedwater heater.
2. A process according to claim 1 where said exhaust gas ranges from a temperature of about 900° to about 1200°F.
3. A process according to claim 1 where said high pressure feedwater heater is supplied with water at a temperature of about 200° to about 500°F at a pressure ranging from about 90 to about 150 atmospheres.
4. A process according to claim 3 where said high pressure steam superheater is supplied with steam at a tempera-ture ranging from about 550° to about 650°F at a pressure ranging from about 90 to about 150 atmospheres and where said steam is superheated by said exhaust gas to a temperature ranging from about 800° to about 1000°F.
5. A process according to claim 4 where said water heated in said high pressure feedwater heater is converted to steam in a separate evaporator and then fed to said high pressure steam superheater.
6. A process according to claim 4 where at least two high pressure feedwater heaters are present.
7. A process for producing high pressure steam using gas turbine exhaust, a waste heat exchanger and a separate evaporator outside said waste heat exchanger comprising passing said exhaust through said waste heat exchanger, where said exhaust first contacts a high pressure steam superheater, and then said exhaust contacts a high pressure feedwater heater.
8. A process according to claim 7 where said water from said high pressure feedwater heater is converted to steam in said separate evaporator and then fed to said high pressure steam superheater.
9. A process according to claim 7 where said exhaust gas ranges from a temperature of about 900° to about 1200°F.
10. A process according to claim 7 where said high pressure feedwater heater is supplied with water at a temperature of about 200° to about 500°F at a pressure ranging from about 90 to about 150 atmospheres.
11. A process according to claim 7 where said high pressure steam superheater is supplied with steam at a temperature ranging from about 550° to about 650°F at a pressure ranging from about 90 to about 150 atmospheres and where said steam is superheated by said exhaust gas to a temperature ranging from about 800° to about 1000°F.
12. A heat recovery system comprising a gas turbine, a waste heat exchanger and a separate evaporator outside said waste heat exchanger wherein said waste heat exchanger comprises means for passing exhaust gas from said turbine to said exchanger, a high pressure steam superheater, and a high pressure feedwater heater.
13. A heat recovery system according to claim 12 further comprising means for passing the liquid heated in said high pressure feedwater heater to said evaporator and means for passing steam formed in said evaporator to said high pressure steam superheater.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/791,175 US4638765A (en) | 1985-10-24 | 1985-10-24 | Heat recovery system |
| US791,175 | 1985-10-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1250749A true CA1250749A (en) | 1989-03-07 |
Family
ID=25152894
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000518328A Expired CA1250749A (en) | 1985-10-24 | 1986-09-16 | Heat recovery system |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US4638765A (en) |
| EP (1) | EP0220954B1 (en) |
| CN (1) | CN1008197B (en) |
| AU (1) | AU589214B2 (en) |
| CA (1) | CA1250749A (en) |
| DE (1) | DE3683009D1 (en) |
| IN (1) | IN167855B (en) |
| NO (1) | NO863879L (en) |
| ZA (1) | ZA867461B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5285629A (en) * | 1992-11-25 | 1994-02-15 | Pyropower Corporation | Circulating fluidized bed power plant with turbine fueled with sulfur containing fuel and using CFB to control emissions |
| US5623822A (en) * | 1995-05-23 | 1997-04-29 | Montenay International Corp. | Method of operating a waste-to-energy plant having a waste boiler and gas turbine cycle |
| US5865369A (en) * | 1995-10-23 | 1999-02-02 | Fisher; Gerald | Recycling high pressure steam for heating purposes |
| US5762031A (en) * | 1997-04-28 | 1998-06-09 | Gurevich; Arkadiy M. | Vertical drum-type boiler with enhanced circulation |
| KR101172422B1 (en) * | 2009-12-11 | 2012-08-08 | 에스케이씨 주식회사 | Waste Heat Recovery System |
| CN105840314B (en) * | 2016-04-26 | 2017-09-19 | 中科合肥微小型燃气轮机研究院有限责任公司 | Test bench for gas turbine gas extraction system with heat storage function |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1312469A (en) * | 1961-10-03 | 1962-12-21 | Babcock & Wilcox France | Improvements to combined cycle steam and gas energy production facilities |
| CH569862A5 (en) * | 1973-10-02 | 1975-11-28 | Sulzer Ag | |
| CH573044A5 (en) * | 1974-01-15 | 1976-02-27 | Sulzer Ag | |
| US3953966A (en) * | 1974-08-08 | 1976-05-04 | Westinghouse Electric Corporation | Combined cycle electric power plant having a control system which enables dry steam generator operation during gas turbine operation |
| US3965675A (en) * | 1974-08-08 | 1976-06-29 | Westinghouse Electric Corporation | Combined cycle electric power plant and a heat recovery steam generator having improved boiler feed pump flow control |
| US4160805A (en) * | 1977-07-14 | 1979-07-10 | Hitachi Shipbuilding & Engineering Co. Ltd. | Boiler containing denitrator |
| US4261167A (en) * | 1979-04-27 | 1981-04-14 | Texaco Inc. | Process for the generation of power from solid carbonaceous fuels |
| US4253300A (en) * | 1979-08-03 | 1981-03-03 | General Electric Company | Supplementary fired combined cycle power plants |
| US4354347A (en) * | 1980-06-02 | 1982-10-19 | General Electric Company | Combined cycle system for optimizing cycle efficiency having varying sulfur content fuels |
| US4353206A (en) * | 1980-08-20 | 1982-10-12 | Westinghouse Electric Corp. | Apparatus for removing NOx and for providing better plant efficiency in combined cycle plants |
| JPS57108402A (en) * | 1980-12-25 | 1982-07-06 | Mitsui Eng & Shipbuild Co Ltd | Equipment for recovering heat of exhaust gas of internal combustion engine |
| US4501233A (en) * | 1982-04-24 | 1985-02-26 | Babcock-Hitachi Kabushiki Kaisha | Heat recovery steam generator |
-
1985
- 1985-10-24 US US06/791,175 patent/US4638765A/en not_active Expired - Lifetime
-
1986
- 1986-09-16 CA CA000518328A patent/CA1250749A/en not_active Expired
- 1986-09-25 IN IN850/DEL/86A patent/IN167855B/en unknown
- 1986-09-29 AU AU63277/86A patent/AU589214B2/en not_active Ceased
- 1986-09-29 NO NO863879A patent/NO863879L/en unknown
- 1986-09-30 ZA ZA867461A patent/ZA867461B/en unknown
- 1986-10-21 CN CN86106910A patent/CN1008197B/en not_active Expired
- 1986-10-24 EP EP86308302A patent/EP0220954B1/en not_active Expired - Lifetime
- 1986-10-24 DE DE8686308302T patent/DE3683009D1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| US4638765A (en) | 1987-01-27 |
| EP0220954A3 (en) | 1988-03-30 |
| NO863879L (en) | 1987-04-27 |
| DE3683009D1 (en) | 1992-01-30 |
| CN86106910A (en) | 1987-04-29 |
| AU6327786A (en) | 1987-04-30 |
| CN1008197B (en) | 1990-05-30 |
| IN167855B (en) | 1990-12-29 |
| NO863879D0 (en) | 1986-09-29 |
| EP0220954A2 (en) | 1987-05-06 |
| EP0220954B1 (en) | 1991-12-18 |
| ZA867461B (en) | 1987-05-27 |
| AU589214B2 (en) | 1989-10-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5623822A (en) | Method of operating a waste-to-energy plant having a waste boiler and gas turbine cycle | |
| EP0391082B1 (en) | Improved efficiency combined cycle power plant | |
| US5357746A (en) | System for recovering waste heat | |
| US6223519B1 (en) | Method of generating power using an advanced thermal recuperation cycle | |
| EP0290220B1 (en) | Reheat type waste heat recovery boiler and power generation plant using the same | |
| US6244033B1 (en) | Process for generating electric power | |
| WO1995012757A1 (en) | Hybrid central receiver | |
| WO1997047866B1 (en) | Hybrid solar and fuel fired electrical generating system | |
| JP2757290B2 (en) | Gas / steam turbine combined facility with coal gasification facility | |
| SU1521284A3 (en) | Power plant | |
| MX173816B (en) | METHODS FOR RECOVERING ENERGY FROM A HIGH GRADE PROCEDURE FROM A CONTACT PROCEDURE FOR THE MANUFACTURE OF SULFURIC ACID | |
| US4637212A (en) | Combined hot air turbine and steam power plant | |
| CA1250749A (en) | Heat recovery system | |
| IL123808A (en) | Energy-generation process and power station for carrying out the process | |
| CS6285A2 (en) | Method of heat and electrical energy simultaneous production especially with industrial power plants | |
| JP3905967B2 (en) | Power generation / hot water system | |
| EP0639254B1 (en) | Method in small-power plant use | |
| US3913330A (en) | Vapor generator heat recovery system | |
| CN209485081U (en) | A kind of waste heat recycling utilization system | |
| RU2776091C1 (en) | Thermal power plant | |
| RU2768325C1 (en) | Thermal power plant | |
| RU2773410C1 (en) | Combined cycle gas plant | |
| JPS6257073B2 (en) | ||
| EP0724683A1 (en) | Integration construction between a steam boiler and a steam turbine and method in preheating of the supply water for a steam turbine | |
| Dechamps et al. | Advanced combined cycle alternatives with advanced gas turbines. |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |